Multiple exhaust generator



y 9, 1934. F. M. BROOKE 7 1,960,691

' MULTIPLE EXHAUST GENERATOR Filed Sept. 2. 1952 e Shets-Sheet 1 WITNESS E5 Jam YWB um'h INVENTOR.

y 9, 1934. F. M. BROOKE 1,960,691

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WITNESS ES y 29, 1934- F. M. BROOKE ,960,691

I MULTIPLE EXHAUST GENERATOR Filed SeptTZ. 1932 e Sheets-'Shet 5 J JGi IZZ FIG. 12

' WITNESSES y 1934- F. M. BROOKE 1,960,691

MULTIPLE EXHAUST GENERATOR Filed Sept. 2. 1932 e Sheets- Sheet 6 FIG-7: 12m

I 5i INVENTOR in mkzwv I Patented May 29, 1934 1,960,691 MULTIYLE EXHAUST GENERATOR Francis M. Brooke, Bryn Mawr, Pa., assignor to Nanna S. Brooke, Bryn Mawr, Pa.

Application SeptemberZ, 1932, Serial No. 631,476

11 Claims.

This invention relates to power generators and more particularly to generators of the type in which theexploded products of combustion are exhausted into a turbine, or other suitable prime mover, for the purpose of operating the same.

Among the objects of this invention I primarily aim to utilize all the energy developed in a combustion chamber, or chambers, by the complete. usage of all the developed pressure against the blades of a turbine, for example. This object is attained by providing the generator combustion chamber, or chambers, with a multiplicityof exhausts which open in series; the decreasing exhaust pressures thereby discharged being applied against successive rows of the turbine blades where, due to expansion, the pressure 'in the turbine is progressively lower. In addition to the foregoing I aim to coordinate a plurality of combustion. chambers either connected -to 'common manifolds, or independent discharge pipes, leading first to the head of the turbine, and successively the other exhausts to the various lower stages of pressure in said turbine. the main object is developed whereby higher pressure can be constantly maintained at the various points of discharge; and pulsation due to sudden changes in pressure in the turbine are eliminated. It is also a further aim of this invention to avoid the necessity inhering to prior combustion chambers of allowing the pressure in the turbine to fall to a low point which prevents the utilization of all of the pressure developed in the combustion chambers in the turbine. A varied and low pressure in the turbine reduces its efficiency. In other words my invention accommodates high minimum pressures at the head, and at I various stages, of the turbine; and yet, at the same time,-utilizes all the pressure energy developed in the combustion chamber or chambers,

free of interference or back pressures, notwithstanding the number thereof, and produces a uniform continuity of explosions that closely approximates the even fluent pressure of steam.

A still further object of my invention is to provide amultiple-exhaust generator which is' struction, and arrangement of parts in a multiple- Thusexhaust generator, as hereinafter described and pointed out in the claims.

In the drawings:-

Figs. I and I, jointly show, in longitudinal side elevation, a combined multi-exhaust and multi-stage turbine embodying the present improvements, with portions broken out or in section to illustrate otherwise hidden structural features; the plane of severance between the two views being designated :c-zc.

Fig. II is an illustration, corresponding to Fig.

I but viewed from the reverse side thereof, with parts broken out, and others in section, to better disclose otherwise obscured features.

.Fig. III is a top plan view of Fig. I. Fig. IV is a plan view of a modifiedform of my invention, more particularly serving to illustrate a duplex series of coordinated combustionchambers with individual exhaust-connections to the turbine. Y

Fig. V is a vertical section of an individual combustion chamber of the multi-exhaust generator. v

Fig. VI is a corresponding section of a coordinated combustion chamber unit but viewed from the reverse side thereof.

Fig. VII is an axial section of a duplex ignitor for interposition between, and for firing a pair of coordinated combustion chambers, such as shown in Figs. V and VI.

Fig. VIII is a detail View of the ignitor sleeve valve. r

Fig. IX is a cross-section, taken on the plane designated IX-IX in Fig. V.

Fig. X is a similar crossesection, taken on the line X--X in Fig. VI. A

plane marked XI-X[ in Fig. VII.

Fig. XII is a plan view of one of the combustion chamber rotary valves, hereinafter fully explained. I

Fig. XIII is an elevation, on a larger scale, of said rotary valve; and,

Fig. XIV is a fragmentary detail view of an automatic valve control for the duplex-ignitor and automatic advance rod for the electric dis tributor.

Referring more in detail to the drawings, my novel multi-exhaust generator comprises, as shown in Figs. I, H and IIImore particularly, a succession of combustion units or chambers each of which is comprehensively designated 1, and as they are similar, except where later on pointed out, the following explanation will be confined to the singular, in order to avoid repeti Fig. In is a like cross-section, taken on the Fig. IV, I may arrange aligned series of combus tion chambers 1,-1a in parallel or flanking the.

turbine 3, but this adaptation of my invention will be hereinafter amplified.

Referring in greater detail to Fig. V, which is a cross-section of one ofthe combustion-oham bers 1, the outer casing is designated 4, while 5 is the space for the circulation of water or other cooling medium, and 6 the inner shell or wall of the combustion chamber 1, said casing and wall being connected by suitable spacers at -various points in the known manner. 7 is a rotary sleeve valve extending the full length of the chamber 1 with provision only of clearance for expansion. The rotary valve '7 has a solid bottom 8 with gear teeth 9, Figs. XII and XIII, by which it is rotated constantly in one direction. This rotary sleeve valve '7 is provided with three spaced ports 10, 11, 12, which are located at different levels or planes and conveniently in vertical alignment, as well as an ignition port 13 that is rectangular,

the long dimension being horizontal or circum-' ferentially disposed so as to allow variation in the time of ignition. A small, accurate, adjustable valve 14 determining the ignition is in the duplex-ignitor 15, which is later described. In

the combustion chamber 1 is an inlet port 16 with which the sleeve valve port 11 registers to permit filling of said combustion chamber with an explosive mixture of air and oil, or gasoline. A port 17 in the combustion chamber 1 registers with the ignition port 13 in the sleeve valve 4 through which, at the proper time, is introduced burning gas, or gas at a higher temperature than the point ofignition from the small. combustion chamber of the ignitor 15, shown in Fig. VII, that is used simply to ignite the mixture in the combustion chamber 1. This provision is made so that fuel oil having a low flash point may be utilized and which will not ordinarily ignite from a spark. The combustion chamber 1 is equipped, however, with a spark plug 18 so that gasoline or other mixture, with a high flash-point, can be readily exploded by an electric spark and the igniter 15 dispensed with, as by turning its valves 14 into a closed position. The position of the rotary sleeve valve 7, in Fig. V, indicates the manner of filling the combustion chamber 1 with gas just preparatory to igniting it.

Fig. V1 is similar to Fig. V, excepting that it shows five relatively-staggered exhaust ports 19, 20, 21, 22 and 23, enumerated in the respective order in which they discharge. As the rotary valve 7 in this view has been turned through one hundred and eighty degrees (180) with respect to the showing on 'Fig. V, its ports 10, 11, 12appear in the center as they do insaid Fig. V. It will be seen that the port 11, in the rotary sleeve valve '7, is registering with the exhaust port 21 of the combustion-chamber lywhile the port 12 followed by port 12 registering with exhaust port 23. Such sequence of opening the combustion chamber exhaust ports 1923, inclusive, affords the exploded gas under pressure opportunity to exhaust through five different and individual outlets for reasons later on fully explained. Attention is directed, at this juncture, to the fact that a greater or lesser number of exhaust ports 19-23 may, if desired, be utilized without departing from the fundamentals of my present invention. The sleeve valve 7, incident to continuous rotation, next moves the port 11 into registration with the port 16, as shown in Fig. V to admit a fresh charge of gas under pressure from the inlet manifold 24, and thus successive cycles are repeated.

Referring now, more particularly to Fig. VII, I have therein shown a single ignitor15 adapted to fire two consecutive combustion chambers 1, so as to minmize complication of the apparatus. This ignitor 15, if provided with more inlet ports,

could possibly fire three, or even a greater number of combustion chambers 1 in rotation, but a point would be ultimately reached that would limit the speed at which the adjustablevalves 14 thereof could be rotated and explosions obta ned in the secondary combustion chambers 1. Each ignitor 15 is fitted with. a sleeve valve 14 having an opening or vertical slot 25, Fig. VIII,

for coaction with an inlet port 26 through the ignitor jacketed wall 27 to admit an explosive mixture under pressure, and an exhaust port 28, which is connected by a conduit 29 into one of the exhaust pipes or manifolds, 44 for example, leading from one of the coordinated combustion chambers 1, see Figs. I and 1, whose time of exhausting is remote from the time of discharge through the auxiliary exhaust port 28.- In similar member the igniter 15 is provided with an inlet port 31, Fig. XI, directly opposite the port 26, and an auxiliary exhaust port 32 likewise opposite the exhaust port 28. The'port 28 is set about thirty degrees (30) to the right or in advance of a main exhaust port 33, and the port 32 likewise about thirty degrees (30) to the right or in advance of another main exhaust port 34. These two ports 33, 34 are exhaust ports from the ignitor 15 to the two attached combustion chambers 1. The ignitor sleeve valve 14 has a base 35 provided with gear teeth 36 by which it is rotated. In this sleeve valve 14 the vertical slot 25 is parallel-to the inlet port 26, and narrower thanthe latter, while there is also a small auxiliary open ng 3'? in said sleeve valve which is adapted to register with the lower part of the exhaust port 28 when opening 25 commences to register with the inlet port 31, so that the'bumed gases will be forced out of the'ignitor 15 by the entering fresh combustible gases. This auxiliary opening 3'7 is located below the lower edge of the main exhaust ports 33, 34, also lower than the bottom edge of the exhaust port 28, so as to prevent leakage by contacts. Port openings 25 and 37, Fig. VIII, are not visible in Fig. VII, as they are through that portion of the wall of the adjustable valve 14 that has been removed by the section cut off. The manifolds 38 act not only as a connection but as a brace and support for action can probably be more readily understood,

said views showing cross-sections along the lines IX--IX, X-X and XI-XI. of Figs. V, VI and VII, respectively. These views show the various 150 ports in the combustion chambers 1 so intersected, likewise those in therotary valves 7 and 14 and the relative positions thereof; with the dotted lines indicating the locations of the ports below the respective planes of intersection.

Referring now to Fig. XIV, I therein illustrate .to and controls the shaft on which-the distributor rotates, the contact points being held in a fixed position. Thus whenthe generator is started at slow speed, the ignition port 13 registers with the port 33 when the port 10 is just about to register with the port 19,. and in the same manner with port 34 when port 10 isabout to register with port 19. As the sleeve valves 7 rotate more rapidly the same interval of time for'combustion and building up of pressure in the combustion chambers 1 is required. Therefore, the adjustable sleeve valve 14 of the ignitor device 15 is moved, say approximately twenty degrees (20) counter-clockwise relative to the a sleeve valve 7 by the automatic governon' It is known that in an ordinary combustion chamber in combination with a turbine, following the opening of the exhaust valve to the turbine, the pressure falls rapidly as the exploded chamber the pressure may be allowed to fall to atmospheric before closing the exhaust valve and thus utilize all the pressure, but the efficiency of the turbine is greatly reduced because of the irregular and low pressure average. Furthermore, it will not run smoothly and will have an uneven torque. With the explosion there will be-a sudden and violent pressure applied to the blades when the turbine would seem to be running at a reduced speed and then there would be an interval where no pressure would be applied to the blades. This poor condition is modified by adding combustion chambers so that there are a successive series of explosions applied and no intervals without pressure being exerted on the turb'ne blades. The ideal situation being such an increase in the number of combustion chambers that the pressure at the turbine head, or in manifold entering the turbine, is always maintained at a. minimum pressure that is fairly high. Iri this way the efficency of the tur-' bine is maintained, while the regularity of the impulses makes it smooth running and the torque becomes even. However, this process in the past has inevitably led to a corresponding, or even greater inefficency on the part of the combustion chambers. v

Let it be assumed, for argument, that there are such a large. number of combustion chambers, say twenty-five or more, with an explosive pressure of four hundred pounds to the square inch at the time the exhaust valves open, with a frequency in the repetition-of the explosions that the pressure in the iiianifolqleadin'g to the turbine, is maintained at a nti'hnuni of three hundred and fifty pounds to the re inch. 7 Possibly the average pressure in the manifold'would be around three hiifiid-red and seventy-pounds. Thus a fairly even high'pressure is accomplished. Y The cost of maintaining.such pressure, however, is prohibitive because, if the pressure in the exhaust manifold is never under three hundred and fifty pounds then the combustion chambers cannot blades.

exhaust below three hundred and fifty pounds and This latter possibility is probably why efforts havebeen made in some other analogous apparatus to take care of the inefliciency of the combustion chamber.

In accordance with my present invention I make use of any convenient number of connected combustion chambers 1', and serially graduate the exhaust pressures therefrom downwardly from an initial high pressure when thefirst exhaust port opens to approximately atmospheric pressure when the last exhaust opens; but certainly to a pressure below that of the'new charges .of

explosive gas admitted into said combustion chambers. The new charges, during-a very short interval being used to partially scavenge out the residual burnt gases of a previous explosion. Obviously, if the size of the manifolds, size and number of the connected combustion chambers,

and particularly the sizes of the respective ports 19-23, are designed for certain predetermined conditions, then by the addition of more exhausts all the pressure in the combustion chambers 1 may be effectively utilized down to almost atmospheric pressure. It will also be readily understood that substantially the same results are obtainable no matter whether the exhausts 19-23 take place into common manifolds respectively, or if individual exhaust pipes are used-as indicated in the showing of Fig. IV.

The important question is how to utilize the pressure stages or five ranges achieved by the five exhausts 19, 20, 21, 22 and 23. The turbine 3, shown in Fig. I is an elevation of a turbine such as is described in my co-pending application for patent SerialNo. 628,509, filed November 4, 1932. which is particularly -3-adaptable for complete expansion of gases with a very high initial temconstruction in common use. This provides a turbine 3, practical for an unusually wide range of temperature. In it the pressure and temperature, due to adiabatic expansion, progressively fall as the gases reach the exhaust of'the turbine 3 where they are comparatively very low. This turbine 3 is particularly adaptable to the principles of the generator herein described. I

The above question is answered by having the first manifold or manifolds 30 connected with the head of the turbine 3 to apply the high pressure directly on the first rows of stator and rotor.

folds 911 from exhausts 20, to be applied to subsequent rows of stator and rotor blades where the pressure in the turbine would fall-by adiabatic expansion to the minimum pressure figured therefor. The turbine 3 is of cone shape and the larger having successively a greater altitude.

Geometric circular rings inscribing various rows of rotor blades become larger as they are taken further from the point of initial entrance of gas The second manifold or series of manirotor and stator blades become progressively into the turbine 3. The reason for the constant increase of the surface area of the rotor blades presented to the gas passing through the turbine is because the pressure has fallen, as the gas has done work in its process of expansion. Thus if additional gas is injected at various successive points along the turbine 3 where the pressure has been decreasing and is injected, at a pressure higher than that at which the gas would be at such a point, without the process of boosting by this additional gas, it is obvious that such new gas can be efficiently utilized in helping to maintain pressure throughout said turbine. Thus in Figures I and I it may be noted that the gas from the first exhaust port 19 enters the turbine head 45 by way of the manifold 30 opposite the first row of blades. In a like manner the gas at a somewhat lower pressure from exhaust port 20 enters the turbine 3 by way of a manifold 41 through injectors or orifices 46 at a point further along the turbine 3 in the direction of the flow of gas, through said turbine where the pressure has decreased below that at which it is leaving the exhaust port 20. Similarly exhaust ports 21 are connected still further down the turbine 3 by a manifold 42, where the pressure is correspondingly lower, through injectors or orifices 46. Exhaust ports 22 are connected by a manifold 43 to a pointapproaching the exhaust end of the turbine 3 where the pressure is quite low. Exhaust ports 23 are connected by a manifold 44 with oriflces or injector heads 46 which are located so near the exhaust end of the turbine 3 that the pressure there. except as stimulated by the gas entering 46, is lower than the pressure of the unexploded gas that is built up by the compressor employed to charge the combustion chambers 1.

In addition the turbine 3 itself has been used to full efliciency in that there has been a high minimum pressure at the initial point of entrance of gas in said turbine and the variation in pressure at this point has been minimized. In a like manner the pressure has been better maintained by boosting at various points which have been 10 .cated where the gas can exhaust itself advantageously and without creating a disadvantageous back pressure. An even pressure can be developed by a multiplicity of consecutive explosions in such rapidityas to approach the even pressure of steam.

It might be mentioned that the turbine 3 receives gas through 30, which in Figs. I and I is shown as a common manifold, and at the other points through a common manifold 41, which is later sub-divided at the various points of the oriflees or injectors 46. In a like manner there are sub-divided manifold exhausts 42, 43, and 44. In

Fig. IV individual exhausts 47, 48, 49, 50 and 51 are employed to the various points of the orifices or injectors 46. A compressor 52 drives gas mixed with fuel oil, of a lowfiash'point, through the manifold 24 to the inlet port 16; while a small compressor 54 drives air mixed with gasoline, of

a high flash point, through a manifold 55 into the ignitor or ignitors' 15 through inlet ports-26 and 31.

Auxiliary exhaust ports 28 and 32 of the igniter 15'are connected in Figs. I and II with the manifold 44 by a pipe 29'. In Fig. IV the exhaust port 28 is connected with manifold 51, of the combustion chamber 1, whose'3time ;fof exhaust is at the greatest interval from the'ope'ning of said exhaust port, which would be relatively that of Fig.

VI, when considering Fig. Conversely the auxiliary exhaust port 32 isv connected with the exhaust 23 of Fig.'VI. In Fig. IV they are connected by pipes 56.

In Figs. I and II the valve shaft 57, which operates worm gears 58, which mesh with teeth 9- Figs. XII and XIII-of the bases 8, of rotary sleeve valves 7, is conveniently driven by a chain 59; and the latter by a sprocket 60 which is driven by an extension shaft 61 from the turbine 3. Likewise the shaft 62 of the small compressor 54 is driven by a chain 63. In Fig. IV the shafts 62, which through worm gears, not shown, similar to 58, meshing with teeth 36 rotate the ignitor sleeve valves 14; said shafts 62 being hidden by the manifolds 30, but the bevel gears 64 .(partly visible) at its end are rotated by a bevel gear 65 on the driving shaft 66. A bevel gear 67 on shaft 66 is rotated by a gear 68 on the shaft 69; while a sprocket '70 on the latter shaft is rotated by a chain drive 71 from a sprocket 72 on extension shaft 61. Suitable shaft bearings are all marked 73; while the shaft 69 carries the automatic valve control comprehensively designated 74, and shown to best advantage in Fig. XIV.

In Fig. IV the chain drives 59 rotate the valves '7 by sprockets 60 on the shafts 5'7, which are hid- 0 den by the manifolds 53. Worm drives 58 on shaft 5'7 Figs. II, XII and XIII mesh with gear teeth 9 on the bases 8 of the rotary sleeve valves 7. In Figs. I and III, a different arrangement is shown, the chain 59 also drives the compressor 52, while in Fig. IV it is limited as above set forth. In Fig. IV chains 75 conduct the power from the extension shaft 61 to both compressors 52, by sprockets '76 on said shaft and sprockets 7'7 on the shafts 78 of the compressors 52. A single chain 63 passing over two sprockets 79 is carried under the extension shaft 61 and meshes with a sprocket 80 on said shaft to drive the compressors 54.

In Fig. XIV I show the combination of a common centrifugal-weight balanced-spring governit, a turn or so relative to the left-hand part of the shaft 69 which has a square end 85 on which the device casing86 slides and is supported. In a like manner as the speed of the shaft 69 slows down, the centrifugal force decreases, the spring 82 expands, forcing the casing 86 in the opposite direction. This reverse pressure-on the internal worm gear 84 rotates the right-hand part of the shaft in an opposite direction which retards the ignitor sleeve valve 14 at slow speed. 87 is a thrust bearing, having one vertical face and one diagonal, which holds the governor device 74 in place, but permits it to rotate relative to the right-hand part of the shaft 69.

In Fig. IV an arm 88 extending outwardly from one of the casings for the shaft bearings 73' supports a conventional electrical distributor 89, stationary. When the automatic control casing 86 moves in one direction to advance the shaft 66 relative to the. shaft 61, it advances the contact point on said shaft 66 for the device 89, and viceversa, whereupon the valves 14 in the ignitor devices 15, are correspondingly advanced or retarded, through the mechanisms hereinbefore described. As a result variation in the timing of ignition under control of a switch-89 is effected,

in a manner well-known in the art. In Figs. I and II the distributor 89 is shown on the shaft, 57 and with similar provisions it will be readily understoodthat advancement of the valves 7, in

the combustion chambers, may be corresponding- Iy effected, and vice-versa. For simplicity electric wiring 90, to the spark plugs 18 and 39, is conventionally indicated in Fig. I, while the lubricating system and water pump connections both for the combustion chambers 1 and the turbine 8 are omitted to avoid confusive illustration.

It may be noted that the arrangement or placing of the combustion chambers 1, relative to the turbine 3, may be made as desired, particularly if individual exhaust pipes 47-51 are used rather than the common manifolds 38 and 41-44.

While I have described somewhat specifically practical embodiments of my invention, it is .to be understood that I do not confine myself to the precise details of construction herein set forth, as it is apparent thatchanges and variations therein may be eifectediby those skilled in-the art without departing from the spirit of said invention, or exceeding the scope of the following claims.

Having thus described my invention, I claim: 1. The combination with a series of combustion chambers and a multi-stage rotary prime mover, of a primary ignitor-device adapted to serve the combustion chambers sequentially, said ignitor device and the respective combustion chambers each including a rotary ported-sleeve means, means to exhaust the products of combustion from the combustion chambers at vary-,

ing pressures, and individual manifolds from said exhausts, connecting into said prime mover, for conducting the developed kineticenergy therefrom at the respective varying pressures for utilization in said prime mover.

2. In a power generator the combination of a pluralty of sequentially-connectible combustion chambers, an ignitor device common to said chambers; individual coaxial rotary sleeve valves in said device and combustion chambers, means for admitting a charge of gaseous mixture into said device, means for igniting such mixture, and said valve and the respective combustion chambers each embodying a multiplicity of coactive ports respectively controlling discharge of the ignited mixture from the device aforesaid into the respective combustion chambers; and individually associated manifolds for taking-off the exploded gas at varying pressures from the combustion chambers;

3. In a power generator and an associated prime mover, the combination of a plurality of cylindric combustion chambers, an ignitor device connect-- ing said chambers in sequence, individual"coaxial rotary sleeve valves in said device and the respective combustion chambers, means for admitting a charge of gaseous mixture into said device, means forigniti'ng such mixture, said ignitor valve- -having spaced ports successively registrable with coactive ports in the walls of the respective combustion chambers for discharge of ignited gas Y therefrom into said combustion chambers, .said

combustion chambers having similar ports controlling individual exhausts of exploded gas therefrom at a varying scale of pressures, and individual manifolds for the several'exhausts connecting into a prime mover for maintaining constant stagewise pressures in said prime mover.

4. In a power generator and an associated prime mover, the combination of a plurality of cylindric combustion chambers, an ignitor device common to and successivelyconnectible into said chambers, a coaxial rotary ported-sleeve valve and means for admitting a charge of gaseous mixture into said device and for discharging ignited gas therefrom into the "respective combustion chamor interfering back pressure.

5. In a power generator and an associated prime mover, the combination of a plurality of cylindric combustion chambers, an ignitor del.

vice common to and sequentially connectible into said chambers, a coaxial rotary ported-sleeve valve and means for admitting a charge of gaseous mixture into said device and for discharging ignited gas therefrom into the respective connected combustion chambers, means for igniting such mixture, a similar valve in each combustion chamber having spaced ports of different areas and in vertical alignment, said ports being successively registrable with staggeringly-arranged ports through the combustion chamber wall for the purpose of controlling individual exhausts of exploded gas from the several combustion chambers at varying pressures, manifolds common to the respective staggering individual exhausts connecting with the prime mover, said individual exhausts being effective to maintain constant I minimum pressures in the prime mover without 110 loss of kinetic energy, and a circumferential horizontal port at the upper part of each combustion chamber rotary valve adapted to control admission of burning gas at a higher temperature from the ignitor device aforesaid to explode gaseous mixturein the associated combustion chamber.

6. In a power generator and an associated prime mover, the combination of an ignitordevice, a plurality of cylindric combustion chambers individually-connected to said device, a coaxial rotary sleeve valve in each combustion chamber with a portcontrolling admissionof a charge of gaseous mixture, an inlet manifold common to all of the combustion chambers supplying the gaseous mixture, means coordinatively operating said valves in timed relation, a. coaxial rotary sleeve valve in the ignitor device with an exhaust port adapted to effect sequential. discharge of the ignited, gaseous mixture therefrom into the connected cylindric combustion chambers to explode gaseous mixture in said chambers, and a multiplicity of coactive ports in the respective combustion chamber and associated'valve walls controlling individual exhausts of the exploded gas at varying pressures from the latter into respectively associated manifolds, and said manifolds individually connecting into the prime mover for the purpose of maintaining constant minimum pressures in said prime mover without loss of kinetic ene gy or any interfering 140 back pressure.

7. In a power generator and an associated prime mover, the combination of a plurality of cylindric combustion chambers, a coaxial rotary sleeve valve in each chamber with a port con- 145 trolling admission of a charge of gaseous mixture, an inlet manifold common to alLof the combustion chambers supplying the gaseous mixture, means coordinatively operating said valves' in timed relation, ignitor-devices each including a 5 similar coaxial rotary valve, said devices being common to predetermined combustion chambers and adapted to discharge successive charges of ignited gas to effect sequential explosion of gaseous mixture in said combustion chambers, a multiplicity of coactive ports in' the respective combustion chambers and coaxial rotary valves controlling individual exhausts of the exploded gas at varying pressures, and associated common manifolds connecting with the' prime mover, whereby the respective individual exhausts are utilized to maintain constant stage-wise-pressures in said prime mover without loss of kinetic energy or any interfering back pressure.

8. In a power generator and an associated rorality of cylindric combustion chambers, a coaxial rotary sleeve valve in each chamber with a port controlling admissip n of a charge of gaseous mixture under pressure, an inlet manifold common to all of the combustion chambers supplying the gaseous mixture, means coordinating said valves for actuation in timed relation, ig-

, nitor-devices each includinga cylindric primary combustion chamber with a coaxial rotary sleeve valve having an inlet port for an ignitible me- .dium, said devices also having exhaust ports 5 connectible into predetermined combustion chambers in sequence, operating means common to all said ignitor devices, a plurality of coactive ports on different planes in theassociated combustion chambers and coaxial sleeve valves controlling individual exhausts of exploded gas therefrom at varying pressures and individual manifolds common to the respective planes of exhaust connecting with the rotary prime mover, whereby the respective individual exhausts are utilized to maintain constant stage-wise pressures in said prime mover without loss of kinetic energy or any interfering back pressure.

9. In a power generator the combination of a ,plurality of cylindric combustion chambers with a common inlet manifold, apoaxial rotary sleeve valve in each chamber for admitting a charge of gaseous mixture under pressure from the common manifold, means coordinating said valves for actuation in sequential relation, ignitor devices each including a cylindric combustion chamber and a coaxial rotary sleeve valve, said devices connecting, with predetermined combustion chambers in sequence, operating means common to all said ignitor devices, a plurality of coactive ports in the respective combustion chambers and amociated rotary valves controllingindividual exhausts of exploded gas therefrom at varying pressures, and manifolds common to the respective individual exhausts for conducting said exhausts into a connected prime mover.

10. In a power generator a sequence of cylindric combustion chambers with a common manifold, intervening ignitor devices adapted to connect with said chambers sequentially, a coaxial rotary sleeve valve in each combustion chamber for admitting a charge of gaseous mixture under pressure from the common manifold, a coaxial rotary valve in each. ignitor device for admitting charges of exploded gas into the associated combustion chambers to ignite the gaseous mixture in the latter, means coordinating all of said valves for actuation in sequential timed. relation, a plurality of coactive ports on differmo em planes of exhaust, and similar coactive exhaust ports in the ignitor devices with a common conduit connection into one bf the last mentioned manifolds.

11. In a power generator a sequence of cylindric combustion chambers with a common inlet manifold, intervening ignitor devices adapted to connect with said chamber sequentially, a coaxial rotary sleeve valve in each combustion chamber for admitting a charge of gaseous mixture under pressure from the common inlet maulfold, a coaxial rotary valve in each ignitor device for admitting charges-of exploded gas into the connected combustion chambers to ignite the gaseous mixture in the latter, means coorditary prime mover, the combination of a plu-' nating all of said valves for actuation in sequential timed relation, a plurality of coactive ports on folds, in combination with means whereby the several rotary valves may be automatically advanced or retarded. I

12. In a power generator, a sequence of cylindric combustion chambers with a common inlet manifold, intervening ignitor devices adapted to connect with said chambers consecutively, a coaxial rotary sleeve valve in each combustion chamber for admitting a charge of gaseous mixture under pressure from the common manifold, a coaxial rotary 'sleeve valve in each ignitor device for intermittently admitting charges of exploded gas into the connected combustion chembers to ignite gaseous mixture in the latter, electrical ignition means for each combustion chamber and ignitor device, means coordinating all of said valves for actuation in sequential timed J relation, a pluralty of coactive ports on different planes in the combustion chambers and coaxial valves controlling individual exhausts of the exploded gas therefrom at varying pressures, manifolds common to the respective planes of the exhausts for conducting such exhausts into a connected prime mover, coactiyeeexhaust ports in the respective ignitor devices having a common conduit connection into one of the last mentioned manifolds to scavenge said ignitor devices, in combination with means whereby the several rotary valves and electrical ignition means may be automatically advanced or retarded.

13. In a power generator, a cylindric combustion chamber with a coaxial rotary sleevevalve admitting a charge of low grade explosive mixture thereinto, means affording individual exhausts of the exploded gas therefrom at varying pressures, a communicating ignitor device with means supplying a charge of high grade mixture thereto, a rotary sleeve valve in the ignitor device having a single port controlling the admission of explosive mixture into and discharge of the buming gases therefrom into the cylindic combustion chamber, said ignitor device also having an auxiliary outlet remote from and in a difl'erent plane than the single inlet-exhaust port to facilitate scavenging of the device, and means connecting said auxiliary outlet into the lowest pressure individual exhaustaforesaid;

14. In a power generator a plurality of combustion chambers with means supplying charges oflowgrade explosive mixture thereto, means affording individual exhausts of the exploded gas therefrom at varying pressures, smaller connected chambers with means to supply and ignite charges of high grade explosive mixture therein, rotary sleeve means with a single port controlling admission of explosive mixture into and discharge of the ignited mixture from said smaller chambers into the several larger combustion c mbers for ignition of the charges in the latter said rotary sleeve means each having an auxiliary outlet remote from and in a different plane to the port aforesaid to facilitate "scavenging of the ignition chamben'said outlets being connected to the-lowest pressure manifold from the larger co bustion chambers, and electrical means cont ling timed ignition of the charges in the smaller combustion chambers.

,15. In a power generator a plurality of combustion chambers withmeans supplying charges of low grade explosive mixture thereto, means affording individual exhausts of the exploded gas therefrom [at varying pressures, smaller connected chambers with means to supply and ignite charges of high grade explosive mixture. therein, rotary sleeve means with a single port controlling admission of explosive mixture into and discharge I of the ignited mixture from, said smaller chambers into the several larger combustion chambers for ignition of the charges in the'latter, said rotary sleeve means each having an auxiliary outlet remote from and in a different plane to the port aforesaid to facilitate scavenging of the ignition chamber, said outlets being connected to the lowest pressure manifold from'the larger combustion chambers, and electrical means controlling timed ignition of the charges in the smaller combustion chambers, in combination with means to angularly rotate the several smaller sleeve valves up to approximately fifty degrees so as to vary the position of the ports therein relative to corresponding ports in the larger combustion chamber sleeve valves.

16. In a power generator a plurality of combustion chambers with means supplying charges of low "grade explosive mixture thereto, means affordingindividual exhausts of the exploded a I therefrom at varying pressures, smaller connected chamberswith) means to supply and ignite charges of high grade explosive mixture therein, rotary sleeve means with a single port controlling admission of explosive mixture into and discharge of the ignited mixture from said smaller chambers into the several largr combustion chambers for ignition of the charges in the latter, said rotary sleeve means each having an auxiliaryl outlet remote from and in a different plane to the port aforesaid to facilitate scavenging of the ignition chamber, said outlets. being connected to the lowest pressure manifold from the larger. com-.

bustion chambers, and electrical means controlling timed ignition of the charges in the smaller combustion chambers, in combination with automatically actuated means effective .to variably shift the smaller sleeve valves'within an'-angle of approximately fifty-degrees to control timing of ignition in 'the larger combustion chambers.

-17. In a power generator, a sequence of, cylindric combustion chambers, a coaxial rotary sleeve valve in each chamber for admitting a charge of gaseous mixture from a common manifold, means coordinatively operating said valves continuously in one direction, ignitor devices connecting predetermined combustion chambers sequentially, means supplying high grade explosive mixture to and electric means for exploding same in said ignitor devices to fire the charges in the cylindric combustion chambers, a plurality of coactive ports in said combustion chambers and associated valves controlling individual exhausts of the exploded gases at varying pressures, and means including a two-part shaft with, associated governor mechanism whereby said shaft parts are movable axially toward or away from each other for rotatively shifting the ignitor device sleeve valves to control admission of a high grade gasand effect correct ignition timing in the cylindric combustion chambers in relation to the varying speed with which the sleeve valves in the latter rotate.

FRANCIS M. BROOH. 

